JP2021161954A - Compressor - Google Patents

Abstract

To provide a compressor which can suppress the vibration of a vane while possessing a flat face at a fixing body face.SOLUTION: A front cam face 103 of a front fixing body 90 has a front recessed face 103a for generating positive acceleration between a first angle position θ1 and a first inflection angle position θM1, and has a front protrusive face 103b for generating negative acceleration between a second angle position θ2 and a second inflection angle position θM2. Also, the front cam face 103 has a front inclination face 104 for setting acceleration to zero between the first inflection angle position θM1 and the second inflection angle position θM2. A first front flat face 101, the front recessed face 103a, the front inclination face 104, the front protrusive face 103b and a second front flat face 102 are continuously formed at a front fixing body face 100 in a peripheral direction in this order.SELECTED DRAWING: Figure 11

Description

The present invention relates to a compressor.

In Patent Document 1, a rotating shaft, a columnar rotor as a rotating body in which a plurality of slit grooves as vane grooves are formed, and a plurality of vanes oscillatingly fitted in the plurality of slit grooves are fixed. An axial vane compressor equipped with a side plate as a fixed body on which a cam surface as a body surface is formed is described. In the axial vane type compressor described in Patent Document 1, a plurality of vanes rotate while moving in the axial direction of the rotating shaft as the rotating shaft and the rotor rotate, so that the axial end surface of the rotor and the cam as the rotating body surface The fluid is sucked and compressed in a compression chamber partitioned by a surface. Further, in Patent Document 1, the cam surface of the side plate connects the top side plane portion, the bottom side plane portion, and the top side plane portion and the bottom side plane portion as a flat surface extending perpendicularly in the axial direction. It is described that the curved surface portion is provided in.

Japanese Unexamined Patent Publication No. 2015-14250

Here, in the configuration in which the vane moves on the cam surface, the acceleration of the vane is constant when the vane passes through the top plane portion and the bottom plane portion, but the acceleration occurs when the vane passes through the curved surface portion. , Vibration may occur due to the occurrence of acceleration.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a compressor capable of suppressing vane vibration while having a flat surface on a fixed body surface.

A compressor for solving the above problems is a compressor that rotates at a constant rotation speed around a rotation axis, and has a rotating body having a rotating body surface that intersects the rotating axis.
A fixed body that does not rotate and has a fixed body surface that faces the rotating body surface and the axial direction in which the rotating axis extends, and three vane grooves formed at positions shifted by 120 ° in the circumferential direction of the rotating body. It includes three vanes that are inserted and rotate while moving in the axial direction with the rotation of the rotating body, and the fixed body surface intersects the axial direction and is 180 ° in the circumferential direction of the rotating body. When a pair of flat surfaces at offset positions and a pair of cam surfaces connecting the pair of flat surfaces are provided and the circumferential position on the fixed body surface is an angular position, the circumferential direction on one of the flat surfaces The intermediate angular position of the cam surface is defined as the first intermediate angular position, the intermediate angular position of the other flat surface in the circumferential direction is defined as the second intermediate angular position, and the angular position of the boundary portion between each cam surface and one flat surface is set. The first angular position is defined, the angular position of the boundary portion between each cam surface and the other flat surface is defined as the second angular position, and the angular position deviated by 60 ° from the first intermediate angular position is defined as the third angular position. The fourth angle position is an angle position shifted by 120 ° from the first intermediate angle position, and the first variation angle position is the angle position shifted by the first angle position from the third angle position to the first intermediate angle position side. Then, from the 4th angle position to the 2nd intermediate angle position side, the angle position deviated by the angle of the 1st angle position is set as the 2nd variation angle position, and from the 2nd angle position to the 2nd intermediate angle position side. The angle position deviated from the first angle position becomes the second intermediate angle position, and the speed change when the vane moves in the axial direction is defined as the acceleration of the vane, and the vane is relative to the rotating body surface. The change in velocity when moving in the positive direction approaching the fixed body surface is defined as a positive acceleration, and the change in velocity when the vane moves in a negative direction away from the fixed body surface relative to the rotating body surface is negative. Each cam surface has a first acceleration surface located between the first angle position and the first variation angle position to generate the positive acceleration, and the second angle position. The second acceleration surface, which is located between the second variation angle position and causes the negative acceleration, is located between the first variation angle position and the second variation angle position, and is said to be the same. It has a constant acceleration surface with zero acceleration, and the fixed body surface has one of the flat surfaces, the first acceleration surface, the constant acceleration surface, the second acceleration surface, and the other flat surface. It is a gist that the surfaces are continuously arranged in the circumferential direction in the above order.

According to such a configuration, before the vane passes through the constant acceleration surface, the acceleration generated when passing through the first angular position which is the boundary between one flat surface and the first acceleration surface, and the first acceleration surface and the constant acceleration surface. A constant positive acceleration is generated on the first acceleration surface while canceling out the acceleration generated when passing through the first variation angle position which is the boundary of the above. Further, after the vane has passed through the constant acceleration surface, the acceleration generated when passing through the second variation angle position which is the boundary between the constant acceleration surface and the second acceleration surface, and the boundary between the second acceleration surface and the other flat surface. A constant negative acceleration is generated on the second acceleration surface while canceling out the acceleration generated when passing through the second angle position. Therefore, the acceleration that occurs before and after the vane passes through the constant acceleration plane can be offset. Then, the acceleration is constant on the surface where the acceleration is constant. Therefore, the acceleration generated from one flat surface to the other flat surface can be suppressed in total. Since the three vanes pass through the fixed body surface in synchronization, the acceleration can be suppressed by each of the three vanes, and the vibration caused by the acceleration can be suppressed as a whole.

For the compressor, the positive acceleration when the vane passes through the first acceleration surface may be constant, and the negative acceleration when the vane passes through the second acceleration surface may be constant.
According to such a configuration, the shapes of the first acceleration surface and the second acceleration surface can be curved surfaces having a constant curvature, and the first acceleration surface and the second acceleration surface can be easily manufactured.

For the compressor, the time required for the positive acceleration to become constant, the time required for the positive acceleration to become zero, the time required for the negative acceleration to become constant, and the negative acceleration to be zero. The time required for the above is the same, and the time when the positive acceleration is constant and the time when the negative acceleration is constant may be the same.

According to this configuration, on the cam surface, the displacement pattern of acceleration from one flat surface through the first acceleration surface to reach the constant acceleration surface, and the other from the constant acceleration surface through the second acceleration surface. The displacement pattern of the acceleration until reaching the flat surface can be made the same in the opposite directions. Therefore, the positive acceleration and the negative acceleration can be canceled out to be zero, and the acceleration can be made zero in cooperation with the zero acceleration on the constant acceleration plane.

According to the present invention, the vibration of the vane can be suppressed while having a flat surface on the fixed body surface.

The schematic diagram which shows the outline of the compressor of an embodiment. An exploded perspective view of the main configuration of the embodiment. An exploded perspective view of the main configuration seen from the side opposite to FIG. FIG. 6 is a cross-sectional view of a main configuration of the compressor of the embodiment. Sectional view of the cylinder. FIG. 6-6 is a cross-sectional view taken along the line 6-6 of FIG. FIG. 7-7 is a cross-sectional view taken along the line 7-7 of FIG. FIG. 8-8 is a cross-sectional view taken along the line 8-8 of FIG. A development view schematically showing a rotating body, both fixed bodies, and a vane. A development view schematically showing a rotating body, both fixed bodies, and a vane. The perspective view which shows the front fixed body. A graph showing the velocity, acceleration, and position of a vane as it makes a half turn. A graph showing the velocity, acceleration, and position of a vane when it makes one revolution. A graph showing the relationship between the accelerations of three vanes.

Hereinafter, an embodiment of the compressor will be described with reference to the drawings. The compressor of the present embodiment is for, for example, a vehicle, and is specifically mounted on a vehicle for use. The compressor is used, for example, in a vehicle air conditioner, and the fluid to be compressed by the compressor is a refrigerant containing oil. For convenience of illustration, the rotating shaft 12, the rotating body 60, and both fixed bodies 90 and 110 are shown in a side view in FIG.

As shown in FIG. 1, the compressor 10 includes a housing 11, a rotating shaft 12, an electric motor 13, an inverter 14, a cylinder 30, a rear plate 40, a rotating body 60, a front fixed body 90, and the like. It is provided with a rear fixed body 110.

The housing 11 has, for example, a cylindrical shape as a whole, and has a suction port 11a and a discharge port 11b into which a suction fluid from the outside is sucked. The rotating shaft 12, the electric motor 13, the inverter 14, the cylinder 30, the rotating body 60, and both the fixed bodies 90 and 110 are housed in the housing 11.

The housing 11 includes a front housing 21, a rear housing 22, an inverter cover 25, a discharge cover 26, and a rear plate 40.
The front housing 21 has a bottomed cylindrical shape and is open toward the rear housing 22. The suction port 11a is provided, for example, at a position on the bottom side of the side wall of the front housing 21 with respect to the open end. However, the position of the suction port 11a is arbitrary.

The rear housing 22 is used in cooperation with the rear plate 40 to partition the storage chamber A3 that houses both the fixed bodies 90 and 110 and the rotating body 60. The rear housing 22 has a bottomed cylindrical shape and is open toward the rear plate 40.

The rear housing 22 has a rear housing bottom portion 23 and a rear housing side wall portion 24 that stands up from the rear housing bottom portion 23 toward the rear plate 40. The front housing 21 and the rear housing 22 are unitized so that the open end of the front housing 21 and the bottom of the rear housing bottom 23 face each other.

As shown in FIGS. 1 and 2, a front insertion hole 23c through which the rotating shaft 12 can be inserted is formed in the bottom portion 23 of the rear housing, and the rotating shaft 12 is inserted through the front insertion hole 23c.

As shown in FIG. 1, the rear housing side wall portion 24 has a rear housing inner peripheral surface 24a which is an inner peripheral surface and a rear housing outer peripheral surface 24b as an outer peripheral surface arranged on a side opposite to the rear housing inner peripheral surface 24a. And have. The inner peripheral surface 24a of the rear housing and the outer peripheral surface 24b of the rear housing are, for example, cylindrical surfaces having the axial direction Z as the axial direction. The inner peripheral surface 24a of the rear housing is separated from the outer peripheral surface of the cylinder 30 in the radial direction R.

The inverter cover 25 is arranged on the side opposite to the rear housing 22 side with respect to the front housing 21. The inverter cover 25 is fixed to the front housing 21 in a state of being abutted against the bottom of the front housing 21. The inverter 14 is housed in the inverter cover 25. The inverter 14 drives the electric motor 13.

The discharge cover 26 is arranged on the side opposite to the rear housing 22 side with respect to the rear plate 40. The discharge cover 26 has a cover bottom portion 26a and a cover side wall portion 26b that stands up from the cover bottom portion 26a toward the rear plate 40. The discharge cover 26 is fixed to the rear plate 40 in a state of being abutted against the rear housing 22 of the rear plate 40. The discharge port 11b is provided on the side wall portion 26b of the cover. However, the position and number of the discharge ports 11b are arbitrary. The discharge chamber A1 in which the compressed fluid exists is partitioned by the outer surface of the rear plate 40 and the discharge cover 26. The discharge chamber A1 in the present embodiment is formed in a disk shape with the axial direction Z as the central axis. The discharge chamber A1 communicates with the discharge port 11b. The compressed fluid in the discharge chamber A1 is discharged from the discharge port 11b to the outside of the housing 11.

As shown in FIGS. 1 to 5, the cylinder 30 is used to accommodate both the fixed bodies 90 and 110 and the rotating body 60. The cylinder 30 has a cylindrical shape formed smaller than the side wall portion 24 of the rear housing. The cylinder 30 has a cylinder inner peripheral surface 31 which is an inner peripheral surface, and a cylinder outer peripheral surface 32 as an outer peripheral surface arranged on a side opposite to the cylinder inner peripheral surface 31. The cylinder inner peripheral surface 31 and the cylinder outer peripheral surface 32 are, for example, cylindrical surfaces having the axial direction Z as the axial direction. In the present embodiment, the cylinder 30 is fixed to the rotating body 60 and rotates integrally with the rotating body 60.

As shown in FIG. 1, the cylinder outer peripheral surface 32 is radially separated from the rear housing inner peripheral surface 24a. In the present embodiment, the accommodation chamber is located between the inner bottom surface 23e which is the inner surface of the rear housing bottom 23, the inner peripheral surface 24a of the rear housing, the first plate surface 43 which is the inner surface of the rear plate 40, and the outer peripheral surface 32 of the cylinder. A3 is partitioned. The accommodation chamber A3 in the present embodiment is formed in a cylindrical shape with the axial direction Z as the axial direction.

Further, a motor chamber A2 partitioned by a front housing 21 and a rear housing bottom 23 is provided in the housing 11, and the electric motor 13 is housed in the motor chamber A2. By supplying drive power from the inverter 14, the electric motor 13 directs the rotating shaft 12 in the direction indicated by the arrow M, in detail, in the clockwise direction when both fixed bodies 90 and 110 are viewed from the electric motor 13. , "Rotation direction M"). The central axis of the rotating shaft 12 is the rotating axis L of the rotating shaft 12. That is, the rotation axis 12 rotates about the rotation axis L.

Incidentally, since the suction port 11a is provided in the front housing 21 that partitions the motor chamber A2, the suction fluid sucked from the suction port 11a is sucked (in other words, introduced) into the motor chamber A2 in the housing 11. That is, the suction fluid exists in the motor chamber A2. That is, it can be said that the motor chamber A2 forms a part of the suction chamber into which the suction fluid is sucked.

In the compressor 10 of the present embodiment, the inverter 14, the electric motor 13, the front fixed body 90, the rotating body 60, and the rear fixed body 110 are arranged in this order in the axial direction Z. However, the positions of these parts are arbitrary, and for example, the inverter 14 may be arranged outside the radial direction R of the rotating shaft 12 with respect to the electric motor 13.

The rear plate 40 has a plate shape (disk shape in the present embodiment), and is sandwiched between the rear housing 22 and the discharge cover 26 so that the plate thickness direction coincides with the axial direction Z. The outer diameter of the rear plate 40 is, for example, the same diameter as the outer peripheral surface of the rear housing outer peripheral surface 24b and the cover side wall portion 26b. Therefore, it can be said that the rear plate 40 constitutes a part of the housing 11.

The rear housing 22 and the rear plate 40 are assembled so that the open end portion of the side wall portion 24 of the rear housing is abutted against the rear plate 40, and the opening of the rear housing 22 is closed by the rear plate 40. Further, the discharge cover 26 and the rear plate 40 are assembled so that the opening end portion of the cover side wall portion 26b is abutted against the rear plate 40, and the opening of the discharge cover 26 is closed by the rear plate 40. ..

Specifically, a plate recess 42 is formed in the rear plate 40 at a position facing the open end of the rear housing side wall 24 in the axial direction Z. The plate recess 42 is formed over the entire circumference. The rear housing 22 and the rear plate 40 are attached to each other in a state where the open end portion of the side wall portion 24 of the rear housing is fitted in the plate recess 42.

The rear plate 40 has a first plate surface 43 and a second plate surface 44 as plate surfaces orthogonal to the axial direction Z. The first plate surface 43 is arranged on the bottom 23 side of the rear housing, and is also the inner surface of the rear plate 40 that partitions the accommodation chamber A3. The second plate surface 44 is arranged on the discharge cover 26 side, and is also the outer surface of the rear plate 40 that partitions the discharge chamber A1. Further, the second plate surface 44 faces the cover bottom portion 26a in the axial direction Z. In the present embodiment, the first plate surface 43 is smaller than the second plate surface 44 because the plate recess 42 is formed.

The compressor 10 includes shaft bearings 51 and 53 that rotatably support the rotating shaft 12.
The front shaft bearing 51 is attached to a boss portion 52 provided at the bottom of the front housing 21. The boss portion 52 has a ring shape protruding from the bottom portion of the front housing 21. The front shaft bearing 51 is arranged inside the radial direction R of the rotating shaft 12 with respect to the boss portion 52, and is the front shaft end of both shaft end portions 12a and 12b which are both ends of the rotating shaft 12 in the axial direction Z. The portion 12a is rotatably supported.

A rear insertion hole 41 through which the rotating shaft 12 is inserted is formed in the central portion of the rear plate 40. The rear insertion hole 41 is formed to be the same as or larger than the rear shaft end portion 12b on the side opposite to the front shaft end portion 12a. The rear shaft end portion 12b is inserted into the rear insertion hole 41.

The rear shaft bearing 53 is provided on the inner wall surface of the rear insertion hole 41 and rotatably supports the rear shaft end portion 12b. The rear shaft bearing 53 is, for example, a coating bearing composed of a coating layer formed on the inner wall surface of the rear insertion hole 41.

The coating layer is arbitrary, and may include, for example, a thermosetting resin or a lubricant. Further, the rear shaft bearing 53 is not limited to the coated bearing formed from the coating layer, and may be any, for example, other sliding bearings or rolling bearings. For convenience of drawing, the rear shaft bearing 53 is shown thicker than it actually is in FIG. 1 and the like.

As described above, in the present embodiment, both shaft end portions 12a and 12b are rotatably supported by both shaft bearings 51 and 53. Here, the point where the front shaft bearing 51 is attached to the boss portion 52 of the front housing 21, and the point where the rear plate 40 on which the rear shaft bearing 53 is formed is sandwiched between the rear housing 22 and the inverter cover 25. In view of the above, it can be said that the rotating shaft 12 is rotatably supported with respect to the housing 11 by both shaft bearings 51 and 53.

As shown in FIG. 1, a storage chamber A3 partitioned by a rear housing 22 and a rear plate 40 is formed in the housing 11, and the rotating body 60 and the rotating body 60 housed in the cylinder 30 are formed in the storage chamber A3. Both fixed bodies 90 and 110 are housed.

The motor chamber A2 and the accommodation chamber A3 are provided side by side in the axial direction Z in the housing 11. The motor chamber A2 and the accommodation chamber A3 are separated by a rear housing bottom portion 23. That is, the rear housing bottom 23 divides the motor chamber A2 and the accommodation chamber A3 so that the suction fluid in the motor chamber A2 does not easily flow into the accommodation chamber A3. The rotating shaft 12 is arranged so as to pass through the bottom portion 23 of the rear housing so as to straddle both the motor chamber A2 and the accommodating chamber A3.

The motor chamber A2 and the accommodation chamber A3 are provided side by side in the axial direction Z in the housing 11. The rotating shaft 12 is arranged so as to pass through the bottom portion 23 of the rear housing so as to straddle both the motor chamber A2 and the accommodating chamber A3.

Next, the rotating body 60 will be described in detail with reference to FIGS. 1 to 4.
The rotating body 60 rotates in the rotation direction M with the rotation of the rotating shaft 12. The rotating body 60 is arranged in the housing 11 so that its rotating axis is the same as the rotating axis L of the rotating shaft 12. That is, the rotating body 60 is arranged so as to be coaxial with the rotating shaft 12, and rotates about the rotating axis L. Therefore, the compressor 10 has a structure of axial motion rather than eccentric motion.

The rotating body 60 includes a rotating body cylinder portion 61 in which the rotating shaft 12 is inserted, and a rotating body ring portion 70 protruding from the rotating body cylinder portion 61 toward the outer side in the radial direction.
The rotating body cylinder portion 61 is attached to the rotating shaft 12 so as to rotate integrally with the rotating shaft 12. As a result, the rotating body 60 rotates with the rotation of the rotating shaft 12. The mounting mode of the rotating body cylinder 61 with respect to the rotating shaft 12 is arbitrary. For example, the rotating body cylinder 61 may be fixed to the rotating shaft 12 by press fitting, or straddles the rotating shaft 12 and the rotating body 61. The rotating body cylinder portion 61 may be fixed to the rotating shaft 12 by the fixing pin inserted in the rotating body. Further, the rotating body cylinder portion 61 and the rotating shaft 12 may be connected by a connecting member such as a key, or the rotating body cylinder portion 61 and the rotating shaft 12 are provided in the recess provided on one side and on the other side. The structure may be such that the convex portions are engaged with each other.

The rotating body cylinder portion 61 has, for example, a cylindrical shape with the axial direction Z as the axial direction. The rotating body cylinder portion 61 has, for example, an inner diameter equal to or larger than that of the rotating shaft 12. The inner peripheral surface of the rotating body cylinder 61 and the outer peripheral surface of the rotating shaft 12 face each other in the radial direction R.

The rotating body cylindrical portion 61 has a tubular tubular portion outer peripheral surface 62 whose axial direction Z is the axial direction. The outer peripheral surface 62 of the tubular portion is curved so as to be convex outward in the radial direction R, and is a cylindrical surface in the present embodiment.

The rotating body ring portion 70 is provided at a predetermined position (near the central portion in the present embodiment) between both rotating body end portions 61a and 61b, which are both ends of the rotating body cylinder portion 61 in the axial direction Z.
The rotating body ring portion 70 is in the shape of an annular plate having an axial direction Z in the plate thickness direction and having a discharge recess 71 formed on the ring outer peripheral surface 70a which is the outer peripheral surface of the rotating body ring portion 70. The discharge recess 71 of the present embodiment extends in the radial direction R with the direction orthogonal to both the axial direction Z and the radial direction R as the circumferential direction, and opens toward the outside of the radial direction R. The rotating body ring portion 70 has a front rotating body surface 71a and a rear rotating body surface 72a as rotating body surfaces on both end faces in the axial direction Z. Both rotating body surfaces 71a and 72a are ring-shaped. Both rotating body surfaces 71a and 72a intersect with respect to the axial direction Z, and are flat surfaces orthogonal to the axial direction Z in the present embodiment. Therefore, the inner peripheral edge and the outer peripheral edge of both rotating body surfaces 71a and 72a are linear when viewed from the radial direction R, and the position in the axial direction Z is constant regardless of the circumferential direction.

The rotating body ring portion 70 has a front inner surface 71b arranged on the opposite side of the front rotating body surface 71a in the axial direction Z, and a rear inner surface 72b arranged on the opposite side of the rear rotating body surface 72a in the axial direction Z. ing. The front inner surface 71b and the rear inner surface 72b are surfaces facing each other in the axial direction Z.

The rotating body ring portion 70 includes a connecting surface 71c that connects the front inner surface 71b and the rear inner surface 72b facing the axial direction Z in the axial direction Z. The connection surface 71c connects the peripheral ends of the front inner surface 71b and the rear inner surface 72b facing the axial direction Z in the axial direction Z.

In the present embodiment, the discharge recess 71 is partitioned by the front inner surface 71b and the rear inner surface 72b facing in the axial direction Z, and a pair of connecting surfaces 71c connecting them. The inner surfaces 71b and 72b are arranged at equal intervals in the circumferential direction, and in detail, they are arranged at positions shifted by 120 ° from each other. In the present embodiment, the rotating body ring portion 70 includes three discharge recesses 71. The three discharge recesses 71 are not displaced in the axial direction Z and are arranged at equal intervals in the circumferential direction.

Further, a vane groove 130 is formed in the rotating body ring portion 70. That is, the rotating body 60 includes a vane groove 130. The vane groove 130 penetrates the rotating body ring portion 70 in the axial direction Z and opens on both rotating body surfaces 71a and 72a. The vane groove 130 of the present embodiment extends in the radial direction R with the direction orthogonal to both the axial direction Z and the radial direction R as the width direction, and opens toward the outside of the radial direction R. Therefore, the vane groove 130 is open to the outer peripheral surface 70a of the ring. The vane groove 130 extends linearly in the axial direction Z.

As a reminder, in the present embodiment, the rotating body ring portion 70 is a portion outside the radial direction R with respect to the rotating body cylinder portion 61. Therefore, the rotating body cylinder portion 61 exists inside the radial direction R of the rotating body ring portion 70. That is, the rotating body ring portion 70 is a portion provided on the outer peripheral surface 62 of the tubular portion and projecting outward from the outer peripheral surface 62 of the tubular portion in the radial direction.

The compressor 10 of the present embodiment includes three discharge recesses 71 and three vane grooves 130. The three discharge recesses 71 and the vane grooves 130 are arranged at equal intervals in the circumferential direction, and in detail, they are arranged at positions shifted by 120 ° from each other. Correspondingly, a plurality of discharge recesses 71 and vanes 131 are arranged at equal intervals in the circumferential direction. Further, the discharge recess 71 and the vane 131 are separated by a certain distance in the circumferential direction. Specifically, the discharge recess 71 and the vane 131 are separated by the thickness of the plate having the connecting surface 71c interposed between them.

The cylinder 30 is fixed to the rotating body 60 so as to rotate integrally. For example, as shown in FIG. 6, the cylinder 30 is fixed to the rotating body 60 by being fastened to the fastening portion 75 provided on the outer peripheral surface 70a of the ring in a state where the fastener 74 penetrates the cylinder 30 in the radial direction R. Has been done. However, the present invention is not limited to this, and the fixing mode of the cylinder 30 and the rotating body 60 is arbitrary, and may be fixed by, for example, press fitting or fitting.

As shown in FIG. 2, the compressor 10 includes a vane 131 inserted into the vane groove 130. The vane 131 has a rectangular plate shape as a whole. The vane 131 is arranged between the fixed bodies 90 and 110, for example, with the plate surfaces of the vane 131 intersecting the circumferential direction of the rotating shaft 12. The vane 131 has a plate shape whose thickness direction is orthogonal to both the width direction of the vane groove 130, that is, the axial direction Z and the radial direction R.

Both plate surfaces of the vane 131 and both side surfaces of the vane groove 130 face each other in the circumferential direction (in other words, the width direction of the vane groove 130). The width of the vane groove 130 (in other words, the facing distance between both side surfaces of the vane groove 130) is the same as or slightly wider than the plate thickness of the vane 131. The vane 131 inserted into the vane groove 130 is sandwiched by both side surfaces of the vane groove 130. The vane 131 is allowed to move axially Z along the vane groove 130. In the present embodiment, both ends of the vane 131, specifically, the vane 131 in the axial direction Z, are in contact with both the fixed body surfaces 100 and 120. Further, the vane 131 is arranged inside the radial direction R of the cylinder inner peripheral surface 31, and faces the cylinder inner peripheral surface 31 in the radial direction R.

As shown in FIG. 4, the compressor 10 includes thrust bearings 81 and 82 that support the rotating body 60 from the axial direction Z. Both thrust bearings 81 and 82 are arranged on both sides of the rotating body cylinder portion 61 in the axial direction Z, and sandwich the rotating body cylinder portion 61 from the axial direction Z.

Specifically, the front thrust bearing 81 is located at the bottom 23 of the rear housing. The front thrust bearing 81 supports the rotating body cylinder portion 61 (specifically, the front rotating body end portion 61a) from the axial direction Z in a state of being supported by the bottom portion 23 of the rear housing.

The rear thrust bearing 82 is arranged in the thrust accommodating recess 83 formed in the rear plate 40. The thrust accommodating recess 83 is formed in a portion of the inner wall surface of the rear insertion hole 41 that is closer to the first plate surface 43 than the second plate surface 44 and a peripheral portion of the rear insertion hole 41 in the first plate surface 43. The rear thrust bearing 82 is arranged in the thrust accommodating recess 83, and supports the rotating body cylinder portion 61 from the axial direction Z in a state of being supported by the rear plate 40.

Both thrust bearings 81 and 82 have a disk shape, and a rotating shaft 12 is inserted through both thrust bearings 81 and 82. In the present embodiment, the inner peripheral surfaces of both thrust bearings 81 and 82 and the outer peripheral surface of the rotating shaft 12 are in contact with each other. In this case, it can be said that both thrust bearings 81 and 82 support the rotating shaft 12 by abutting the rotating shaft 12 in the radial direction R. However, the present invention is not limited to this, and both thrust bearings 81 and 82 and the rotating shaft 12 may be separated from each other in the radial direction R.

Both fixed bodies 90 and 110 are arranged on both sides of the rotating body ring portion 70 in the axial direction Z. In other words, it can be said that the both fixed bodies 90 and 110 are arranged so as to face each other with the rotating body ring portions 70 separated from each other in the axial direction Z, and the rotating body ring portions 70 are between the both fixed bodies 90 and 110. It can be said that it is located in. The front fixed body 90 is a fixed body arranged closer to the motor chamber A2 than the rotating body ring portion 70 and the rear fixed body 110, and the rear fixed body 110 is closer than the rotating body ring portion 70 and the front fixed body 90. It is a fixed body arranged at a position away from the motor chamber A2.

The front fixed body 90 is a fixed body arranged near the bottom 23 of the rear housing among both fixed bodies 90 and 110, and the rear fixed body 110 is attached to the rear plate 40 of both fixed bodies 90 and 110. It can be said that it is a fixed body arranged at a close position.

The configurations of both fixed bodies 90 and 110 will be described in detail. In this embodiment, both the fixed bodies 90 and 110 have the same shape.
As shown in FIGS. 1 to 4, the front fixed body 90 of the two fixed bodies 90 and 110 is, for example, ring-shaped (annular in the present embodiment), and the front fixed body insertion hole into which the rotating shaft 12 is inserted is inserted. Has 91. In the present embodiment, the front fixed body insertion hole 91 is a through hole penetrating in the axial direction Z. The front fixed body 90 is arranged in the cylinder 30 with the rotating shaft 12 inserted into the front fixed body insertion hole 91.

The front fixed body 90 has a surface that intersects the radial direction R and has a cylinder inner peripheral surface 31 and a front fixed body outer peripheral surface 92 that faces the radial direction R. In the present embodiment, the outer peripheral surface 92 of the front fixed body and the inner peripheral surface 31 of the cylinder are in contact with each other.

The front fixing body 90 includes a front back surface 93 facing the bottom portion 23 of the rear housing and the axial direction Z. The front back surface 93 and the inner bottom surface 23e of the rear housing bottom portion 23 may be separated from each other or may be in contact with each other.

Of the two fixed bodies 90 and 110, the rear fixed body 110 is ring-shaped (annular in the present embodiment) like the front fixed body 90, and has a rear fixed body insertion hole 111 into which the rotating shaft 12 is inserted. doing. In the present embodiment, the rear fixed body insertion hole 111 is a through hole penetrating in the axial direction Z. The rear fixed body 110 is arranged in the cylinder 30 with the rotating shaft 12 inserted into the rear fixed body insertion hole 111. That is, in the present embodiment, the rotating shaft 12 penetrates both the fixed bodies 90 and 110 in the axial direction Z.

The rear fixed body 110 has a surface that intersects the radial direction R and has a cylinder inner peripheral surface 31 and a rear fixed body outer peripheral surface 112 that faces the radial direction R. In the present embodiment, the outer peripheral surface 112 of the rear fixed body and the inner peripheral surface 31 of the cylinder are in contact with each other. That is, the cylinder inner peripheral surface 31 of the present embodiment faces the ring outer peripheral surface 70a and the outer peripheral surfaces 92 and 112 of both fixed bodies in the radial direction R.

The rear fixed body 110 includes a first plate surface 43 of the rear plate 40 and a rear back surface 113 facing the axial direction Z. The rear back surface 113 and the first plate surface 43 may be separated from each other or may be in contact with each other.

As shown in FIG. 4, the rotating body 60 is supported by both fixed bodies 90 and 110 by inserting the rotating body cylinder portion 61 into the fixed body insertion holes 91 and 111 of both fixed bodies 90 and 110. Specifically, of the both rotating body end portions 61a and 61b which are both ends of the rotating body cylinder portion 61 in the axial direction Z, the front rotating body end portion 61a is inserted into the front fixed body insertion hole 91 and is fixed to the front. It penetrates the front fixed body 90 through the body insertion hole 91.

The front fixed body insertion hole 91 is formed so as to correspond to the rotating body cylinder portion 61 (specifically, the outer peripheral surface 62 of the cylinder portion), and in the present embodiment, the rotating body cylinder portion 61 corresponds to a cylindrical shape. It is formed in a circular shape when viewed from the axial direction Z. The diameter of the front fixed body insertion hole 91 may be the same as or slightly larger than the diameter of the outer peripheral surface 62 of the tubular portion. The front rotating body end 61a is rotatably supported by the front fixing body 90 by a front rotating body bearing (not shown) formed on the inner wall surface of the front fixing body insertion hole 91.

Similarly, of the two rotating body end portions 61a and 61b, the rear rotating body end portion 61b on the side opposite to the front rotating body end portion 61a is inserted into the rear fixed body insertion hole 111, and the rear fixed body insertion hole 111. It penetrates the rear fixed body 110 through.

The rear fixed body insertion hole 111 is formed so as to correspond to the rotating body cylinder portion 61 (specifically, the outer peripheral surface 62 of the cylinder portion), and in the present embodiment, the rotating body cylinder portion 61 corresponds to the cylindrical shape. It is formed in a circular shape when viewed from the axial direction Z. The diameter of the rear fixed body insertion hole 111 may be the same as or slightly larger than the diameter of the outer peripheral surface 62 of the tubular portion. The rear rotating body end portion 61b is rotatably supported by the rear fixed body 110 by a rear rotating body bearing (not shown) formed on the inner wall surface of the rear fixed body insertion hole 111.

That is, the end portions 61a and 61b of both rotating bodies are supported by both fixed bodies 90 and 110 via the bearings of both rotating bodies. As a result, the rotating body 60 is supported with respect to both the fixed bodies 90 and 110, and the displacement of the rotating body 60 with respect to both the fixed bodies 90 and 110 can be suppressed.

Further, both rotating body end portions 61a and 61b form both end portions of the rotating body 60 in the axial direction Z. Therefore, it can be said that both end portions of the rotating body 60 are supported by the double rotating body bearings. As a result, the rotating body 60 is stably held.

Further, since the fixed body insertion holes 91 and 111 are formed so as to correspond to the rotating body cylinder portion 61, there is a gap formed between the inner wall surface of the fixed body insertion holes 91 and 111 and the outer peripheral surface 62 of the cylinder portion. It is unlikely to occur or the gap is small.

Incidentally, the rotating body bearing is, for example, a coating bearing composed of a coating layer formed on the inner wall surface of the fixed body insertion holes 91 and 111. The specific configuration of the rotating body bearing is not limited to the coated bearing, and may be arbitrary, for example, other sliding bearings or rolling bearings.

The front fixed body 90 has a front fixed body surface 100 as a fixed body surface facing the front rotating body surface 71a and the axial direction Z. The front fixed body surface 100 is a plate surface on the opposite side of the front back surface 93. The front fixed body surface 100 has a ring shape, and in the present embodiment, it is annular when viewed from the axial direction Z.

As shown in FIG. 3, the front fixed body surface 100 is a pair of front surfaces as cam surfaces connecting the first front flat surface 101 and the second front flat surface 102 orthogonal to the axial direction Z and both front flat surfaces 101 and 102. It has a cam surface 103.

As shown in FIG. 1, both front flat surfaces 101 and 102 are displaced in the axial direction Z. Specifically, the second front flat surface 102 is arranged at a position closer to the front rotating body surface 71a than the first front flat surface 101, and is in contact with the front rotating body surface 71a. The surfaces of the front fixed body surface 100 other than the second front flat surface 102 are separated from the front rotating body surface 71a in the axial direction Z.

Both front flat surfaces 101 and 102 are arranged apart from each other in the circumferential direction of the front fixed body 90, for example, they are displaced by 180 °. In this embodiment, both front flat surfaces 101 and 102 are fan-shaped. In the following description, the circumferential positions of both fixed bodies 90 and 110 are also referred to as angular positions.

The pair of front cam surfaces 103 are each fan-shaped. As shown in FIG. 3, the pair of front cam surfaces 103 are arranged to face each other in the direction orthogonal to both the axial direction Z and the opposite directions of both front flat surfaces 101 and 102. Both front cam surfaces 103 have the same shape.

The pair of front cam surfaces 103 connect both front flat surfaces 101 and 102, respectively. Specifically, one of the pair of front cam surfaces 103 connects one ends of both front flat surfaces 101 and 102 in the circumferential direction, and the other end of both front flat surfaces 101 and 102 in the circumferential direction. The other ends on the opposite side of the part are connected to each other.

Here, for convenience of explanation, the angle position of the boundary portion between the front cam surface 103 and the first front flat surface 101 is set to the first angle position θ1, and the angle of the boundary portion between the front cam surface 103 and the second front flat surface 102. Let the position be the second angle position θ2. For convenience of illustration, the angular positions θ1 and θ2 are shown by broken lines in FIG. 3, but the boundary portions are actually smoothly continuous.

The front cam surface 103 is a cam surface displaced in the axial direction Z according to the circumferential direction (in other words, the angular position of the front fixed body 90). Specifically, the front cam surface 103 is displaced in the axial direction Z so as to gradually approach the front rotating body surface 71a from the first angle position θ1 to the second angle position θ2. In other words, the pair of front cam surfaces 103 are provided on both sides in the circumferential direction with respect to the second front flat surface 102, and gradually separate from the front rotating body surface 71a as the distance from the second front flat surface 102 in the circumferential direction increases. Is displaced in the axial direction Z.

In the present embodiment, the front cam surface 103 has a front concave surface 103a that is curved in the axial direction Z so as to be concave with respect to the front rotating body surface 71a and an axial direction that is convex toward the front rotating body surface 71a. It has a front convex surface 103b that is curved in Z.

The front concave surface 103a is arranged closer to the first front flat surface 101 than the second front flat surface 102, and the front convex surface 103b is arranged closer to the second front flat surface 102 than the first front flat surface 101. Has been done. The angle range occupied by the front convex surface 103b and the angle range occupied by the front concave surface 103a are the same. The front concave surface 103a and the front convex surface 103b are curved surfaces having a constant curvature.

Further, the thickness of the front fixed body 90 (in other words, the length in the axial direction Z) is different depending on the angular position. Specifically, the portion of the front fixed body 90 corresponding to the second front flat surface 102 is the thickest, and the portion corresponding to the first front flat surface 101 is the thinnest. The portion of the front fixed body 90 corresponding to the front cam surface 103 gradually becomes thinner from the second front flat surface 102 toward the first front flat surface 101.

As shown in FIG. 1 or 2, the rear fixed body 110 has a rear fixed body surface 120 as a fixed body surface facing the rear rotating body surface 72a in the axial direction Z. The rear fixed body surface 120 is a plate surface on the side opposite to the rear back surface 113. The rear fixed body surface 120 has a ring shape when viewed from the axial direction Z, and is annular in the present embodiment.

In the present embodiment, the rear fixed body surface 120 has the same shape as the front fixed body surface 100. The rear fixed body surface 120 is a pair of rear cams as cam surfaces connecting the first rear flat surface 121 and the second rear flat surface 122 intersecting the axial direction Z (orthogonal in the present embodiment) and both rear flat surfaces 121 and 122. It has a surface 123 and.

As shown in FIG. 1, both rear flat surfaces 121 and 122 are displaced in the axial direction Z. Specifically, the second rear flat surface 122 is arranged at a position closer to the rear rotating body surface 72a than the first rear flat surface 121, and is in contact with the rear rotating body surface 72a. The surfaces of the rear fixed body surface 120 other than the second rear flat surface 122 are separated from the rear rotating body surface 72a in the axial direction Z.

Both rear flat surfaces 121 and 122 are arranged apart from each other in the circumferential direction of the rear fixed body 110, and for example, they are displaced by 180 °. In this embodiment, both rear flat surfaces 121 and 122 are fan-shaped.

The pair of rear cam surfaces 123 are each fan-shaped. The pair of rear cam surfaces 123 are arranged to face each other in the direction orthogonal to both the axial direction Z and the opposite directions of the two rear flat surfaces 121 and 122. One of the pair of rear cam surfaces 123 connects one end portions of both rear flat surfaces 121 and 122 in the circumferential direction, and the other side of both rear flat surfaces 121 and 122 opposite to the one end portion in the circumferential direction. The other ends of the are connected to each other.

In other words, the pair of rear cam surfaces 123 are provided on both sides in the circumferential direction with respect to the second rear flat surface 122, and gradually separate from the rear rotating body surface 72a as the distance from the second rear flat surface 122 in the circumferential direction increases. It is displaced in the axial direction Z.

In the present embodiment, the rear cam surface 123 has a rear concave surface 123a that is curved in the axial direction Z so as to be concave with respect to the rear rotating body surface 72a, and an axial direction Z so as to be convex toward the rear rotating body surface 72a. It has a rear convex surface 123b that is curved to the surface.

The rear concave surface 123a is arranged closer to the first rear flat surface 121 than the second rear flat surface 122, and the rear convex surface 123b is arranged closer to the second rear flat surface 122 than the first rear flat surface 121. Has been done. The angle range occupied by the rear convex surface 123b and the angle range occupied by the rear concave surface 123a are the same.

As shown in FIG. 1, both fixed body surfaces 100 and 120 face each other with a phase shift from each other in the axial direction Z via a rotating body ring portion 70. The second front flat surface 102 and the second rear flat surface 122 are arranged so as to be offset in the circumferential direction, and are arranged so as to be offset by 180 ° in the present embodiment. Therefore, the front contact point Pf, which is the contact point between the second front flat surface 102 and the front rotating body surface 71a, and the rear contact point, which is the contact point between the second rear flat surface 122 and the rear rotating body surface 72a. It is arranged so as to be offset from Pr in the circumferential direction. In this embodiment, both contact points Pf and Pr are offset by 180 °. The front contact portion Pf is fan-shaped like the second front flat surface 102, and the rear contact portion Pr is fan-shaped like the second rear flat surface 122.

The facing distance between the two fixed body surfaces 100 and 120 is constant regardless of their angular position (in other words, the circumferential position). Specifically, as shown in FIG. 4, the first front flat surface 101 and the second rear flat surface 122 face each other in the axial direction Z, and the second front flat surface 102 and the first rear flat surface 121 It faces the axial direction Z. The amount of deviation in the axial direction Z between the two front flat surfaces 101 and 102 is the same as the amount of deviation between the two rear flat surfaces 121 and 122. Hereinafter, the amount of deviation in the axial direction Z between the two front flat surfaces 101 and 102 and the amount of deviation between the two rear flat surfaces 121 and 122 are simply referred to as "the amount of deviation".

Further, the displacement of the front cam surface 103 and the displacement of the rear cam surface 123 are the same. That is, the front cam surface 103 and the rear cam surface 123 are displaced in the same direction so that the facing distance does not fluctuate according to the angular position. As a result, the facing distance between the fixed body surfaces 100 and 120 is constant at any angle position.

The specific shapes of the first rear flat surface 121, the second rear flat surface 122, and the rear cam surface 123 are the same as those of the first front flat surface 101, the second front flat surface 102, and the front cam surface 103. , Detailed description is omitted.

Here, the circumferential direction of both the fixed bodies 90 and 110 and the rotating body 60 and the circumferential direction of the rotating shaft 12 coincide with each other, and the radial direction of both the fixed bodies 90 and 110 and the rotating body 60 and the radial direction of the rotating shaft 12. It coincides with R, and the axial direction of both the fixed bodies 90 and 110 and the rotating body 60 and the axial direction Z of the rotating shaft 12 coincide with each other. Therefore, the circumferential direction, radial direction R, and axial direction Z of the rotating shaft 12 may be appropriately read as the circumferential direction, radial direction, and axial direction of the rotating body 60, and the circumferential direction and diameter of both fixed bodies 90 and 110. It may be read as a direction and an axial direction.

As shown in FIG. 4, the compressor 10 includes compression chambers A4 and A5 in which fluid is sucked and compressed. Both compression chambers A4 and A5 are provided in the accommodation chamber A3, and are specifically arranged on both sides of the rotating body ring portion 70 in the axial direction Z. Both compression chambers A4 and A5 are separated from each other in the axial direction Z.

The front compression chamber A4 is partitioned by using a front rotating body surface 71a and a front fixed body surface 100, and in the present embodiment, the front compression chamber A4 is partitioned by these surfaces, a cylinder inner peripheral surface 31 and a cylinder outer peripheral surface 62.

The rear compression chamber A5 is partitioned by using a rear rotating body surface 72a and a rear fixed body surface 120, and in the present embodiment, the rear compression chamber A5 is partitioned by these surfaces, a cylinder inner peripheral surface 31 and a cylinder outer peripheral surface 62. In the present embodiment, the front compression chamber A4 and the rear compression chamber A5 have the same size.

As shown in FIG. 1, the compression chambers A4 and A5 become narrower in the axial direction Z as they approach the contact points Pf and Pr. In other words, the compression chambers A4 and A5 gradually expand in the axial direction Z from the contact points Pf and Pr toward the flat surfaces 101 and 121, and from the flat surfaces 101 and 121 toward the contact points Pf and Pr. As a result, it gradually narrows in the axial direction Z.

Here, since the flat surfaces 102 and 122 are arranged so as to be offset in the circumferential direction, the front compression chamber A4 and the rear compression chamber A5 are out of phase with each other. That is, both compression chambers A4 and A5 are out of phase of the volume change. Specifically, the volume change of the rear compression chamber A5 is phase-lagging with respect to the volume change of the front compression chamber A4.

According to such a configuration, the vane 131 rotates in the rotation direction M as the rotating body 60 rotates. In this case, the vane 131 moves in the axial direction Z along both the fixed body surfaces 100 and 120 (in other words, swings) due to the contact with the both fixed body surfaces 100 and 120. That is, the vane 131 rotates while moving in the axial direction Z. As a result, the vane 131 enters the front compression chamber A4 and the rear compression chamber A5. That is, it can be said that the vane groove 130 rotates the vane 131 with the rotation of the rotating body 60 so that the vane 131 is arranged across both the compression chambers A4 and A5.

Then, in both the compression chambers A4 and A5, the vane 131 causes a periodic volume change with the rotation of the rotating body 60, and the fluid is sucked and compressed, respectively. That is, it can be said that the vane 131 causes a volume change in both the compression chambers A4 and A5.

The moving distance (in other words, the swinging distance) of the vane 131 is the amount of displacement in the axial direction Z between the two front flat surfaces 101 and 102 (or between the two rear flat surfaces 121 and 122), that is, the amount of displacement. Further, the vane 131 is continuously in contact with the surfaces 100 and 120 of both fixed bodies during the rotation of the rotating body 60, which may cause intermittent contact, specifically, periodic separation or contact. Hateful.

Here, as shown in FIG. 7, the front compression chamber A4 is divided into three parts chambers, that is, a first front compression chamber A4a, a second front compression chamber A4b, and a third front compression chamber A4c by three vanes 131. Has been done.

For convenience of explanation, the parts chamber arranged on the front side in the rotation direction M with respect to the second front flat surface 102 among the three parts chambers is referred to as the first front compression chamber A4a.
Further, of the three parts chambers, the parts chamber arranged on the rear side in the rotation direction M with respect to the first front compression chamber A4a is referred to as the second front compression chamber A4b. At least a part of the second front compression chamber A4b is arranged on the rear side in the rotation direction M with respect to the second front flat surface 102.

Further, of the three parts chambers, the parts chamber arranged between the first front compression chamber A4a and the second front compression chamber A4b in the circumferential direction is referred to as the third front compression chamber A4c. The third front compression chamber A4c is arranged on the front side in the rotation direction M with respect to the first front compression chamber A4a and on the rear side in the rotation direction M with respect to the second front compression chamber A4b.

Each of the front compression chambers A4a to A4c is formed over an angle range of 120 °. That is, each of the front compression chambers A4a to A4c extends in the circumferential direction, and the extension length (specifically, the length in the circumferential direction) is a length corresponding to an angle range of 120 °.

Strictly speaking, when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the vanes 131 have not entered the front compression chamber A4. In this case, the spaces on both sides of the vane 131 in contact with the second front flat surface 102 are partitioned by the front contact portion Pf and sealed by the front contact portion Pf. Therefore, even when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the front compression chamber A4 is divided into three parts chambers. In the present embodiment, for convenience of explanation, even when one of the plurality of vanes 131 is in contact with the second front flat surface 102, the front compression chamber A4 is provided by the three vanes 131 to form each front compression chamber A4a. It is assumed that it is partitioned into ~ A4c.

Next, the configuration related to the suction of the suction fluid and the discharge of the compressed fluid into the compression chambers A4 and A5 will be described. Note that FIGS. 9 and 14 schematically show the rotating body 60, the fixed bodies 90, 110, the vane 131, and the ports 140, 145, 150, and 155, and the retainers 147 and 157 are not shown.

As shown in FIG. 2 or 4, the compressor 10 includes a suction communication port 221 for sucking the suction fluid into the storage chamber A3. In the present embodiment, the compressor 10 includes a plurality of suction communication ports 221. The suction communication port 221 is formed in, for example, the rear housing 22, and specifically extends in the axial direction Z so as to straddle both the rear housing bottom portion 23 and the rear housing side wall portion 24. The suction communication port 221 is open to the motor chamber A2 and is open to the accommodation chamber A3. The motor chamber A2 and the accommodation chamber A3 are communicated with each other by the suction communication port 221.

The suction fluid sucked (in other words, introduced) from the suction port 11a into the motor chamber A2 is sucked into the accommodation chamber A3 (in other words, introduced) through the suction communication port 221. That is, the suction fluid exists in the accommodation chamber A3. That is, it can be said that the accommodation chamber A3 forms a part of the suction chamber into which the suction fluid is sucked.

The compressor 10 includes a front suction port 140 as a suction passage for sucking the suction fluid into the front compression chamber A4. The front suction port 140 communicates the motor chamber A2 and the front compression chamber A4 by penetrating the bottom 23 of the rear housing and the front fixing body 90 in the axial direction Z.

Specifically, the front suction port 140 has a bottom suction hole 141 penetrating the bottom 23 of the rear housing in the axial direction Z, and a front fixed body suction hole 142 penetrating the front fixing body 90 in the axial direction Z. There is. The bottom suction hole 141 and the front fixed body suction hole 142 overlap in the axial direction Z and communicate with each other. The bottom suction hole 141 is formed in the same fan shape as the front fixed body suction hole 142 in the radial direction R and the circumferential direction.

As shown in FIG. 9, when the vane 131 moves from the second front flat surface 102 in the rotation direction M, the front contact portion Pf and the vane 131 start to form the first front compression chamber A4a. The front fixed body suction hole 142 is provided on the front side in the rotation direction M with respect to the second front flat surface 102. In the present embodiment, the front fixed body suction hole 142 extends in the circumferential direction at the front cam surface 103 on the front side in the rotation direction M with respect to the second front flat surface 102.

As shown in FIG. 8, the front fixed body suction hole 142 of the present embodiment has, for example, an oval shape in which the circumferential direction is the longitudinal direction and the radial direction R is the lateral direction. The front fixed body suction hole 142 is formed between both ends of the front fixed body surface 100 in the radial direction R, and the front fixed body surface 100 exists on both sides of the front fixed body suction hole 142 in the radial direction R. .. As a result, both ends of the vane 131 in the radial direction R passing over the front suction port 140 (specifically, the front fixed body suction hole 142) are supported by the front fixed body surface 100. Therefore, it is possible to prevent the vane 131 from sinking into the front suction port 140.

In the present embodiment, the front fixed body suction hole 142 extends in the rotation direction M from the angle position on the front side of the rotation direction M with respect to the front contact portion Pf. The front fixed body suction hole 142 has an arc shape when viewed from the axial direction Z, and the circumferential length of the front fixed body suction hole 142 is, for example, less than or equal to the circumferential length of each of the front compression chambers A4a to A4c. Yes, in this embodiment, it is shorter than the circumferential length of each of the front compression chambers A4a to A4c. That is, the circumferential length of the front fixed body suction hole 142 is shorter than the distance between the vanes 131, in other words, the angle range in which the front fixed body suction hole 142 is formed is smaller than 120 °.

The front fixed body suction hole 142 of the present embodiment is formed inside the radial R of the front fixed body outer peripheral surface 92 so as not to be arranged at the portion outside the radial direction R with respect to the ring outer peripheral surface 70a.

As shown in FIGS. 2, 7 or 9, the compressor 10 opens and closes a front discharge port 145 that discharges the compressed fluid compressed in the front compression chamber A4 to the discharge recess 71, and a front that opens and closes the front discharge port 145. It includes a discharge valve 146 and a front retainer 147 that adjusts the opening degree of the front discharge valve 146. Note that FIG. 9 schematically shows the front discharge port 145, the rotating body ring portion 70, and the vane 131, and the front retainer 147 is not shown. The front discharge port 145 communicates with the front compression chamber A4 and the discharge recess 71 by opening the front rotating body surface 71a.

The front discharge port 145 is provided in the rotating body ring portion 70. The front discharge port 145 communicates the front rotating body surface 71a and the front inner surface 71b in the axial direction Z. The front discharge port 145 communicates the front compression chamber A4 with each discharge recess 71 by penetrating the rotating body ring portion 70 in the axial direction Z.

In the present embodiment, a plurality of front discharge ports 145 are provided in the rotating body ring portion 70, and are arranged in the circumferential direction of the rotating body ring portion 70. Each of the plurality of front discharge ports 145 is circular. However, the shape of the front discharge port 145 is arbitrary. For example, the front discharge port 145 may have an oval shape or the like. In a configuration in which a plurality of front discharge ports 145 are provided, the sizes of the front discharge ports 145 may be the same or different.

In the present embodiment, the front discharge port 145 is arranged adjacent to the vane groove 130 on the front side in the rotation direction M. Further, the front discharge port 145 is provided in the rotating body ring portion 70 with a certain distance in the rotation direction of the rotating body ring portion 70 with respect to the vane groove 130. Therefore, the front discharge port 145 and the vane groove 130 rotate while maintaining a state of being spaced apart in the circumferential direction as the rotating body 60 rotates. The front compression chambers A4a to A4c are always in communication with the front discharge port 145 as the rotating body 60 rotates.

Here, focusing on the relationship between the suction / compression in the front compression chamber A4 and the front contact portion Pf, as shown in FIG. 9, in the space on the front side in the rotation direction M with respect to the front contact portion Pf, While the suction fluid is always sucked, the fluid is always compressed in the space on the rear side in the rotation direction M with respect to the front contact portion Pf. That is, the front compression chamber A4 is provided on the front side of the rotation direction M with respect to the front contact portion Pf, and is in the rotation direction M with respect to the suction space Sf1 in which the suction fluid is sucked and the front contact portion Pf. It includes a compression space Sf2 provided on the rear side and where fluid is compressed. Then, the front discharge port 145 discharges the compressed fluid compressed in the compression space Sf2 to the discharge recess 71 in the rotating body ring portion 70 by opening to the front rotating body surface 71a. As a result, the compressed fluid compressed in the front compression chamber A4 is introduced into the discharge recess 71.

In the present embodiment, the suction space Sf1 is composed of the first front compression chamber A4a when the vane 131 is in contact with the second front flat surface 102, and the vane 131 is in contact with the second front flat surface 102. If not, it is composed of a first front compression chamber A4a and a space on the front side in the rotation direction M with respect to the front contact portion Pf in the second front compression chamber A4b. The suction space Sf1 gradually widens in the axial direction Z as the distance from the front contact portion Pf in the circumferential direction increases. The volume of the suction space Sf1 increases with the rotation of the vane 131.

Focusing on the relationship with the suction space Sf1, at least a part of the front fixed body suction hole 142 is provided on the front side in the rotation direction M with respect to the front contact portion Pf so as to communicate with the suction space Sf1. It can be said that there is.

The compression space Sf2 is composed of a second front compression chamber A4b, and more specifically, is a space on the rear side of the front contact portion Pf in the second front compression chamber A4b in the rotation direction M. In other words, the compression space Sf2 is a space surrounded by a vane 131 that separates the second front compression chamber A4b and the third front compression chamber A4c and the front contact portion Pf.

Incidentally, regardless of the position (phase) of the vane 131, the compression space Sf2 and the suction space Sf1 are sealed by the front contact portion Pf. As a result, leakage of the compressed fluid from the compressed space Sf2 to the suction space Sf1 is regulated. That is, the front contact portion Pf functions as a sealing portion that regulates the movement of the fluid from the compression space Sf2 to the suction space Sf1.

In the present embodiment, since the circumferential length of the second front compression chamber A4b is longer than the circumferential length of the second front flat surface 102, the second front compression chamber A4b has the suction space Sf1 and the suction space Sf1 depending on the phase. Both of the compressed spaces Sf2 may be configured.

As shown in FIG. 1, the front discharge valve 146 and the front retainer 147 are provided on the front inner surface 71b. The front discharge valve 146 is provided in the discharge recess 71 and opens and closes the front discharge port 145. The front discharge valve 146 and the front retainer 147 are fixed to the rotating body ring portion 70 by being screwed to the front inner surface 71b with the bolt B penetrating both the front discharge valve 146 and the front retainer 147. ..

The front discharge valve 146 has a long plate shape in which the first end portion in the longitudinal direction is fixed to the front inner surface 71b and the front discharge port 145 is opened and closed at the second end portion in the longitudinal direction. The length of the front discharge valve 146 extends along the circumferential direction of the rotating body ring portion 70. It can be said that the front discharge valve 146 is housed in the discharge recess 71 because its length extends in the circumferential direction.

The front discharge valve 146 normally closes the front discharge port 145, and opens when the pressure in the second front compression chamber A4b (specifically, the compression space Sf2) exceeds the threshold value to block the front discharge port 145. To the state where the front discharge port 145 is opened. As a result, the compressed fluid compressed in the front compression chamber A4 is discharged into the discharge recess 71. In this case, the opening angle of the front discharge valve 146 is regulated by the front retainer 147.

As shown in FIG. 8, similarly to the front compression chamber A4, the rear compression chamber A5 has three vanes 131 on the rear side in the rotation direction M with respect to the first rear compression chamber A5a and the first rear compression chamber A5a. It is partitioned into a second rear compression chamber A5b arranged in the first rear compression chamber A5a and a third rear compression chamber A5c arranged in the front side in the rotation direction M with respect to the first rear compression chamber A5a.

Further, the rear compression chamber A5 has a suction space Sr1 provided on the front side in the rotation direction M with respect to the rear contact portion Pr and a compression space Sr2 provided on the rear side in the rotation direction M with respect to the rear contact portion Pr. And, including. The suction fluid is sucked into the suction space Sr1, and the fluid is compressed in the compression space Sr2.

The first rear compression chamber A5a, the second rear compression chamber A5b, and the third rear compression chamber A5c are the same as the first front compression chamber A4a, the second front compression chamber A4b, and the third front compression chamber A4c, and have a rear suction space. Since Sr1 and the rear compression space Sr2 are the same as the front suction space Sf1 and the front compression space Sf2, detailed description thereof will be omitted.

As shown in FIGS. 4 and 8, the compressor 10 includes a rear suction port 150 as a suction passage for sucking the suction fluid into the rear compression chamber A5. Specifically, the rear suction port 150 has a peripheral suction hole 151 that opens to the outer peripheral surface 112 of the rear fixed body and communicates with the accommodation chamber A3, and the peripheral suction hole 151 that communicates with the peripheral suction hole 151 inside the rear fixed body 110. It has a rear fixed body suction hole 152 that penetrates the rear fixed body 110 in the axial direction Z.

The peripheral suction hole 151 is opened to the accommodation chamber A3 at the rear fixed body outer peripheral surface 112. The peripheral suction hole 151 extends in the circumferential direction on the outer peripheral surface 112 of the rear fixed body. The rear fixed body suction hole corresponds to the movement of the vane 131 from the second rear flat surface 122 in the rotation direction M so that the first rear compression chamber A5a is formed by the rear contact portion Pr and the vane 131. The 152 is provided on the front side in the rotation direction M with respect to the second rear flat surface 122. In the present embodiment, the rear fixed body suction hole 152 extends in the circumferential direction at the rear cam surface 123 on the front side in the rotation direction M with respect to the second rear flat surface 122.

The rear fixed body suction hole 152 of the present embodiment has, for example, an oval shape in which the circumferential direction is the longitudinal direction and the radial direction R is the lateral direction. The rear fixed body suction hole 152 is formed between both ends of the rear fixed body surface 120 in the radial direction R, and the rear fixed body surface 120 exists on both sides of the rear fixed body suction hole 152 in the radial direction R. .. As a result, both ends of the vane 131 in the radial direction R passing over the rear suction port 150 (specifically, the rear fixed body suction hole 152) are supported by the rear fixed body surface 120. Therefore, it is possible to prevent the vane 131 from sinking into the rear suction port 150.

In the present embodiment, the rear fixed body suction hole 152 has an arc shape when viewed from the axial direction Z, and the circumferential length of the rear fixed body suction hole 152 is, for example, the circumferential direction of each of the rear compression chambers A5a to A5c. In this embodiment, it is shorter than the circumferential length of each of the rear compression chambers A5a to A5c. That is, the circumferential length of the rear fixed body suction hole 152 is shorter than the distance between the vanes 131, in other words, the angle range in which the rear fixed body suction hole 152 is formed is smaller than 120 °.

The rear fixed body suction hole 152 is provided in a portion on the front side in the rotation direction M with respect to the rear contact portion Pr. Here, as described above, since both the contact points Pf and Pr are displaced in the circumferential direction, the suction holes 142 and 152 of both fixed bodies are also arranged so as to be displaced in the circumferential direction. In the present embodiment, the suction holes 142 and 152 of both fixed bodies are arranged so as to be offset by 180 °.

As shown in FIGS. 1, 8 or 9, the compressor 10 opens and closes a rear discharge port 155 that discharges the compressed fluid compressed in the rear compression chamber A5 into the discharge recess 71, and a rear that opens and closes the rear discharge port 155. It includes a discharge valve 156 and a rear retainer 157 that adjusts the opening degree of the rear discharge valve 156. The rear discharge port 155 is formed at a position facing the front discharge port 145 in the axial direction Z with the discharge recess 71 sandwiched in the axial direction Z.

The specific configurations of the rear discharge port 155, the rear discharge valve 156, and the rear retainer 157 are basically the front discharge port 145, the front discharge valve 146, and the front retainer 147, except that the positions where they are provided are different. Since it is the same as the above, a detailed description will be omitted. Further, "front" in the description of the front discharge port 145, the front discharge valve 146 and the front retainer 147 described above may be read as "rear".

As shown in FIGS. 4 and 6, the compressor 10 is provided in the rotating shaft 12 and the rotating body 60, and includes a discharge mechanism 170 that connects the discharge recess 71 and the discharge chamber A1.
The discharge mechanism 170 is provided in the rotating shaft 12 and the rotating body 60, and communicates the discharge recess 71 with the discharge chamber A1. The discharge mechanism 170 includes an in-axis passage 171 formed on the rotating shaft 12 as a passage forming shaft member, and a communication hole 172. The in-shaft passage 171 is a passage formed by a part of the rotating shaft 12 having a hollow shape. The in-shaft passage 171 is open to the end face of the rotating shaft 12 in the axial direction Z. The in-shaft passage 171 extends in the axial direction Z so as to be arranged inside the radial direction R of each discharge recess 71.

The communication hole 172 communicates the discharge recess 71 with the in-shaft passage 171 by penetrating the rotating shaft 12 in the radial direction R. A part opening 172a for communicating the discharge recess 71 and the communication hole 172 is formed on the outer peripheral surface 62 of the cylinder portion. The part opening 172a is formed in a region of the outer peripheral surface 62 of the tubular portion for partitioning the discharge recess 71. That is, the part opening 172a is open to the discharge recess 71. The communication hole 172 is a through hole that extends inward in the radial direction R from the part opening 172a and thus penetrates the rotating body cylinder portion 61 and the rotating shaft 12 in the radial direction R.

Therefore, the rotating shaft 12 is inserted into the rotating body cylinder portion 61 and rotates integrally with the rotating body cylinder portion 61, and extends in the axial direction Z and communicates with the discharge chamber A1. It can be said that the shaft has a communication hole 172 for communicating the in-shaft passage 171 and the discharge recess 71.

In the present embodiment, a plurality of communication holes 172 are provided, and more specifically, they are provided at positions shifted by 120 ° in the circumferential direction of the rotating body cylinder portion 61. The compressed fluid that has flowed into each discharge recess 71 is introduced into the discharge chamber A1 via the part opening 172a, the communication hole 172, and the in-shaft passage 171. Further, in the present embodiment, the plurality of communication holes 172 are arranged in parallel in the circumferential direction of the rotating body 60 without being displaced from each other in the axial direction Z. Each discharge recess 71 communicates with the in-shaft passage 171 via a communication hole 172.

As shown in FIG. 9, the compressed fluid compressed in the second front compression chamber A4b pushes away the front discharge valve 146 and is discharged from the front discharge port 145 to the discharge recess 71. Further, the compressed fluid compressed in the second rear compression chamber A5b pushes the rear discharge valve 156 away from the discharge recess 71 having a phase shifted by 180 ° from the discharge recess 71 in which the compressed fluid is discharged, and discharges the rear. It is discharged from port 155.

Then, the compressed fluid introduced into the discharge recess 71 is introduced into the in-shaft passage 171 through the part opening 172a and the communication hole 172, and is introduced into the discharge chamber A1 through the in-shaft passage 171. Therefore, the compressed fluid compressed in the front compression chamber A4 and the compressed fluid compressed in the rear compression chamber A5 are introduced into the discharge chamber A1 through a discharge path having the same length. ing.

As shown in FIG. 2, the vane 131 of the present embodiment is composed of a plurality of parts. Specifically, the vane 131 includes a vane body 132 inserted into the vane groove 130 and two tip seals 133 attached to both ends of the vane body 132 in the axial direction Z. Both tip seals 133 form both ends of the vane 131 in the axial direction Z, and the tip seals 133 come into contact with the fixed body surfaces 100 and 120.

When the rotating shaft 12 is rotated by the electric motor 13, the rotating body 60 rotates accordingly. As a result, the plurality of vanes 131 rotate while moving in the axial direction Z along both the fixed body surfaces 100 and 120 while maintaining their circumferential positions.

For example, in FIGS. 9 and 10, the plurality of vanes 131 move downward while moving in the left-right direction of the paper surface. As a result, volume changes occur in the front compression chambers A4a to A4c and the rear compression chambers A5a to A5c, and the fluid is sucked or compressed. That is, it can be said that the vane 131 rotates while moving in the axial direction Z to suck and compress the fluid in both the compression chambers A4 and A5.

Specifically, in the space on the front side in the rotation direction M from the front contact portion Pf in the second front compression chamber A4b and the first front compression chamber A4a, the volume increases and the suction fluid is sucked from the port 140. It is said.

On the other hand, in the compression space Sf2 and the third front compression chamber A4c, which are spaces on the rear side in the rotation direction M from the front contact portion Pf in the second front compression chamber A4b, the volumes decrease as the rotating body 60 rotates. Then, the suction fluid is compressed. Specifically, the suction fluid is compressed in the third front compression chamber A4c, and the fluid compressed in the third front compression chamber A4c is further compressed in the compression space Sf2.

Then, when the pressure in the compression space Sf2 exceeds the threshold value, the front discharge valve 146 is opened, and the compressed fluid compressed in the compression space Sf2 flows to the discharge recess 71 via the front discharge port 145. The compressed fluid flowing through the discharge recess 71 flows into the discharge chamber A1 via the part opening 172a, the communication hole 172, and the in-shaft passage 171. The same applies to the rear compression chamber A5.

Next, both cam surfaces 103 and 123 will be described in detail.
As shown in FIG. 11, the intermediate position in the circumferential direction of the first front flat surface 101 is defined as the first intermediate angle position θ01. Further, the intermediate position in the circumferential direction of the second front flat surface 102 is set as the second intermediate angle position θ02. In the present embodiment, the first intermediate angle position θ01 is 0 °, and the second intermediate angle position θ02 is 180 °.

The angle between the first intermediate angle position θ01 and the first angle position θ1 is the angle x of the first angle position θ1, and the angle between the second intermediate angle position θ02 and the second angle position θ2 is the angle of the second angle position θ2. As for the angle, the angle of the second angle position is the same as the angle x of the first angle position θ1. Note that the "same" angles include slight deviations due to manufacturing tolerances and manufacturing errors.

On each front cam surface 103, an angle position deviated by 60 ° in the circumferential direction from the first intermediate angle position θ01 is defined as a third angle position θ3. Further, on each front cam surface 103, an angle position deviated by 120 ° in the circumferential direction from the first intermediate angle position θ01 is referred to as a fourth angle position θ4. Since both front cam surfaces 103 have the same shape, the third angle position θ3 and the fourth angle position θ4 are at the same angular position in the circumferential direction on both front cam surfaces 103.

On each front cam surface 103, the angle position deviated by the angle x of the first angle position θ1 from the third angle position θ3 to the first intermediate angle position θ01 side is defined as the first variation angle position θM1. Further, the angle position deviated by the angle x of the first angle position θ1 from the fourth angle position θ4 to the second intermediate angle position θ02 side is defined as the second bending angle position θM2. The angle position deviated by the angle x of the first angle position θ1 from the second angle position θ2 to the second intermediate angle position θ02 side is the second intermediate angle position θ02.

Since the angle x of the first angle position θ1 and the angle x of the second angle position θ2 are the same, the length in the circumferential direction from the first intermediate angle position θ01 to the first variation angle position θM1 and the second intermediate position. The length from the angle position θ02 to the second variation angle position θM2 in the circumferential direction is the same.

In FIG. 11, each angle position θ3 and θ4 is shown by a solid line in order to distinguish them from each angle position θ1 and θ2, but in reality, the boundary portion is smoothly continuous. The inflection angle positions θM1 and θM2 are indicated by a two-dot chain line to distinguish them from the angle positions θ1, θ2, θ3, and θ4, but in reality, the boundary portion is smoothly continuous.

In each front cam surface 103, the front concave surface 103a as the first acceleration surface is between the first angle position θ1 and the first variation angle position θM1, and between the second angle position θ2 and the second variation angle position θM2. Is the front convex surface 103b as the second acceleration surface.

Further, the front cam surface 103 has a front inclined surface 104 between the first inflection angle position θM1 and the second inflection angle position θM2. The front inclined surface 104 is a constant acceleration surface located between the front concave surface 103a and the front convex surface 103b. Therefore, on each front fixed body surface 100, the first front flat surface 101, the front concave surface 103a, the front inclined surface 104, the front convex surface 103b, and the second front flat surface 102 are continuously arranged in the circumferential direction in the above order. ing.

In the present embodiment, the front concave surface 103a and the front inclined surface 104 are continuous in the circumferential direction at a constant inclination angle, and the front inclined surface 104 and the front convex surface 103b are continuous in the circumferential direction at a constant inclination angle. .. That is, it can be said that both front cam surfaces 103 approach the front fixed body surface 100 at a constant inclination angle between the front concave surface 103a, the front inclined surface 104, and the front convex surface 103b.

FIG. 12 shows the acceleration of the vane 131 in the axial direction Z at each angular position when the vane 131 rotates from the first intermediate angle position θ01 to the second intermediate angle position θ02, and shows the acceleration of the vane 131 in the axial direction Z. The velocity is indicated by a one-dot chain line, and the position of the vane 131 in the axial direction Z is indicated by a two-dot chain line.

Further, in FIG. 13, the acceleration in the axial direction Z of the vane 131 at each angular position when the vane 131 rotates the front fixed body surface 100 from the first intermediate angle position θ01 by 360 ° is shown by a solid line, and the axial direction of the vane 131 is shown. The velocity of Z is indicated by a chain line, and the position of the vane 131 in the axial direction Z is indicated by a chain line.

For convenience of explanation, in the following description, unless otherwise specified, the velocity and acceleration mean the velocity and acceleration in the axial direction Z. Further, the speed is set to be "positive" in the direction in which the vane 131 approaches the front fixed body surface 100 relative to the front rotating body surface 71a, and the vane 131 is relatively separated from the front fixed body surface 100 with respect to the front rotating body surface 71a. The direction is "negative". Acceleration is defined as "positive" when the velocity changes in the positive direction, and "negative" when the velocity changes in the negative direction. That is, the acceleration is defined as "positive" when the velocity is rising to the right and "negative" when the velocity is falling to the right.

As shown in FIG. 12 or 13, when the vane 131 passes from the first intermediate angle position θ01 to the first angle position θ1, the vane 131 passes through the first front flat surface 101, so that the vane 131 passes in the axial direction of the vane 131. There is no move to Z. Therefore, the velocity of the vane 131 is zero and the acceleration is zero.

When the vane 131 passes through the first angular position θ1, the vane 131 starts moving in the axial direction Z at the inflection point from the first front flat surface 101 to the front concave surface 103a, so that it is constant positive. Acceleration occurs. The time required for the acceleration of the vane 131 to become constant is defined as the "arrival time T". After that, the vane 131 passes through the front concave surface 103a under a constant acceleration with equal acceleration. The acceleration generated when the vane 131 passes through the front concave surface 103a is positive. In other words, it can be said that the acceleration generated when the vane 131 passes through the front concave surface 103a is "positive".

When the vane 131 passes through the first inflection angle position θM1, a constant negative acceleration is generated due to the inflection from the front concave surface 103a to the front inclined surface 104. However, since the front inclined surface 104 is inclined at a constant inclination angle, the vane 131 accelerates to zero at a constant speed after passing through the first inflection angle position θM1. Therefore, the acceleration generated when passing through the first angle position θ1 which is the boundary between the first front flat surface 101 and the front concave surface 103a and the first bending angle position θM1 which is the boundary between the front concave surface 103a and the front inclined surface 104. It can be said that a constant positive acceleration is generated on the front concave surface 103a while canceling out the acceleration generated when passing through.

The time required for the vane 131 from positive acceleration to zero acceleration is the same as the arrival time T. As a result, the displacement pattern of the acceleration from the first front flat surface 101 through the front concave surface 103a to reach the front inclined surface 104 is represented by the rectangular shape shown in FIG. 12 or FIG.

Further, when the vane 131 passes through the front inclined surface 104 and passes through the second inflection angle position θM2, a constant negative acceleration is generated due to the change from the front inclined surface 104 to the front convex surface 103b. After that, the vane 131 passes through the front convex surface 103b under a constant acceleration with equal acceleration. The acceleration generated when the vane 131 passes through the front convex surface 103b is negative. In other words, it can be said that the acceleration generated when the vane 131 passes through the front convex surface 103b is "negative". Further, the time required for the negative acceleration of the vane 131 to become constant is the same as the arrival time T.

Then, when the vane 131 passes through the second angular position θ2, the movement of the vane 131 in the axial direction Z is stopped at the inflection point from the front convex surface 103b to the second front flat surface 102, so that the vane 131 is constant. Positive acceleration occurs. After that, since the vane 131 moves from the second angle position θ2 to the second intermediate angle position θ02, the vane 131 accelerates to zero at a constant speed after passing through the second angle position θ2. Therefore, the acceleration generated when passing through the second variation angle position θM2 which is the boundary between the front inclined surface 104 and the front convex surface 103b and the second angle position θ2 which is the boundary between the front convex surface 103b and the second front flat surface 102. A constant negative acceleration is generated on the front convex surface 103b while canceling out the acceleration generated when passing through.

Since the vane 131 passes through the second front flat surface 102, the vane 131 does not move in the axial direction Z. Therefore, the velocity of the vane 131 is zero and the acceleration is zero. The time required for the vane 131 from negative acceleration to zero acceleration is the same as the arrival time T. As a result, the displacement pattern of the acceleration from the front inclined surface 104 to the front convex surface 103b and reaching the second front flat surface 102 is represented by the rectangular shape shown in FIG. 12 or FIG.

The time when the vane 131 passes through the front concave surface 103a and the positive acceleration is constant is the same as the time when the vane 131 passes through the front convex surface 103b and the negative acceleration is constant. Therefore, the displacement pattern of the acceleration from the first front flat surface 101 through the front concave surface 103a to reach the front inclined surface 104 and the second front flat surface 102 from the front inclined surface 104 through the front convex surface 103b. The displacement pattern of the acceleration until it reaches is represented by a rectangular shape having the same area, although it is positive and negative. That is, the accelerations that occur before and after the vane 131 passes through the front inclined surface 104 are offset.

As shown in FIG. 13, when the vane 131 passes through the second front flat surface 102 from the second intermediate angle position θ02 to the second angle position θ2, the vane 131 passes through the second front flat surface 102. There is no movement of the vane 131 in the axial direction Z. Therefore, the velocity of the vane 131 is zero and the acceleration is zero.

When the vane 131 passes through the second angular position θ2, the vane 131 starts moving in the axial direction Z at the inflection point from the second front flat surface 102 to the front convex surface 103b, so that it has a constant negative value. Acceleration occurs. After that, the vane 131 passes through the front convex surface 103b under a constant acceleration with equal acceleration. The acceleration generated when the vane 131 passes through the front convex surface 103b is negative. In other words, it can be said that the acceleration generated when the vane 131 passes through the front convex surface 103b is "negative". The time required for the negative acceleration of the vane 131 to become constant is the same as the arrival time T.

When the vane 131 passes through the second inflection angle position θM2, a constant positive acceleration is generated as the vane 131 changes from the front convex surface 103b to the front inclined surface 104. However, since the front inclined surface 104 is inclined at a constant inclination angle, the vane 131 accelerates to zero at a constant speed after passing through the second inflection angle position θM2. Therefore, the acceleration generated when passing through the second angle position θ2 which is the boundary between the second front flat surface 102 and the front convex surface 103b and the second bending angle position θM2 which is the boundary between the front convex surface 103b and the front inclined surface 104. A constant negative acceleration is generated on the front convex surface 103b while canceling out the acceleration generated when passing through.

The time required for the vane 131 from negative acceleration to zero acceleration is the same as the arrival time T. As a result, the displacement pattern of the acceleration from the second front flat surface 102 to the front inclined surface 104 through the front convex surface 103b is represented by the rectangular shape shown in FIG.

Further, when the vane 131 passes through the front inclined surface 104 and passes through the first inflection angle position θM1, a constant positive acceleration is generated due to the change from the front inclined surface 104 to the front concave surface 103a. After that, the vane 131 passes through the front concave surface 103a under a constant acceleration with equal acceleration. The acceleration generated when the vane 131 passes through the front concave surface 103a is positive. In other words, it can be said that the acceleration generated when the vane 131 passes through the front concave surface 103a is "positive". Further, the time required for the positive acceleration of the vane 131 to become constant is the same as the arrival time T.

Then, when the vane 131 passes through the first angular position θ1, the movement of the vane 131 in the axial direction Z is stopped at the inflection point from the front concave surface 103a to the first front flat surface 101, so that the vane 131 is constant. Negative acceleration occurs. After that, since the vane 131 moves from the first angle position θ1 to the first intermediate angle position θ01, the vane 131 accelerates to zero at a constant speed after passing through the first angle position θ1. Therefore, the acceleration generated when passing through the first bending angle position θM1 which is the boundary between the front inclined surface 104 and the front concave surface 103a and the first angle position θ1 which is the boundary between the front concave surface 103a and the first front flat surface 101. A constant positive acceleration is generated on the front concave surface 103a while canceling out the acceleration generated when passing through.

After that, since the vane 131 passes through the first front flat surface 101 from the first angle position θ1 to the first intermediate angle position θ01, the vane 131 does not move in the axial direction Z. Therefore, the velocity of the vane 131 is zero and the acceleration is zero. The time required for the vane 131 from positive acceleration to zero acceleration is the same as the arrival time T. As a result, the displacement pattern of the acceleration from the front inclined surface 104 to the front concave surface 103a and reaching the first front flat surface 101 is represented by the rectangular shape shown in FIG.

The time when the negative acceleration is constant when the vane 131 passes through the front convex surface 103b is the same as the time when the positive acceleration is constant when the vane 131 passes through the front concave surface 103a. Therefore, the displacement pattern of the acceleration from the second front flat surface 102 through the front convex surface 103b to reach the front inclined surface 104, and from the front inclined surface 104 through the front concave surface 103a to the first front flat surface 101. The displacement pattern of the acceleration until it reaches is represented by a rectangular shape having the same area, although it is positive and negative. That is, the accelerations that occur before and after the vane 131 passes through the front inclined surface 104 are offset.

As shown in FIG. 12 or 13, when one vane 131 makes one rotation of the fixed body surface 100 from the first intermediate angle position θ01 of the first front flat surface 101, paying attention to the acceleration of the vane 131, one piece The vane 131 moves at an acceleration of "positive"-> "zero"-> "negative"-> "negative"-> "zero"-> "positive".

The one vane 131 does not accelerate by passing through the front inclined surface 104, but the front inclined surface 104 has the first front flat surface 101 and the front concave surface 103a, the front convex surface 103b, and the second front flat surface 102. Since it is located between, the graph of acceleration when the vane 131 passes from the first intermediate angle position θ01 to the second intermediate angle position θ02 shows a region of zero acceleration, that is, a reciprocity across the front inclined surface 104. It is expressed in the direction of Then, the graph sandwiching the region of zero acceleration is represented as point symmetry centered on the middle of the region of zero acceleration. With the front fixed body surface 100 having such a configuration, it can be said that the accelerations can be canceled out to zero while one vane 131 passes through the front fixed body surface 100.

In the present embodiment, the three vanes 131 are moving at the same time while maintaining a state in which the front fixed body surface 100 is shifted by 120 °. The vane 131 that starts moving from the first intermediate angle position θ01 of the first front flat surface 101 is defined as the first vane 131a, and the vane 131 is located at a position shifted forward by 120 ° in the rotation direction M with respect to the first vane 131a. Is the second vane 131b, and the vane 131 located at a position shifted forward by 240 ° in the rotation direction M with respect to the first vane 131a is the third vane 131c. In FIG. 14, the acceleration of the first vane 131a is shown by a solid line, the acceleration of the second vane 131b is shown by a long-dashed line, and the acceleration of the third vane 131c is shown by a long-dashed line.

FIG. 14 shows the displacement of the acceleration of each vane 131 until the first to third vanes 131a to 131c rotate 360 ° from the first intermediate angle position θ01. As shown in FIG. 14, the first vane 131a moves while generating an acceleration of “positive” → “zero” → “negative” → “negative” → “zero” → “positive”. The second vane 131b moves while generating an acceleration of “negative” → “negative” → “zero” → “positive” → “positive” → “zero”. The third vane 131c moves while generating an acceleration of “zero” → “positive” → “positive” → “zero” → “zero” → “positive”.

When the first vane 131a passes through the front concave surface 103a of one front cam surface 103, the second vane 131b passes through the front convex surface 103b of one front cam surface 103 and the third vane 131c. Passes through the other front inclined surface 104. Therefore, the accelerations of the three vanes 131 become "positive", "negative", and "zero", and are canceled in total. Alternatively, when the first vane 131a passes through the front convex surface 103b of one front cam surface 103, the second vane 131b passes through the other front inclined surface 104 and the third vane 131c Passes through the front concave surface 103a of one front cam surface 103. Therefore, the accelerations of the three vanes 131 become "negative", "zero", and "positive", and are canceled in total.

In this way, the inclination of the front cam surface 103 is adjusted so that the acceleration of the three vanes 131 always takes a combination of "positive", "negative", and "zero". The rear inclined surface 124 is also provided on the rear cam surface 123. Since the specific configuration of the rear cam surface 123 including the rear inclined surface 124 is basically the same as that of the front cam surface 103 including the front inclined surface 104, detailed description thereof will be omitted. Further, "front" in the above description of the front cam surface 103 and the front inclined surface 104 may be read as "rear".

According to the present embodiment described in detail above, the following effects are obtained.
(1) On the fixed body surfaces 100 and 120, the first angular position θ1 and the first variable angle position θM1 are provided with the concave surfaces 103a and 123a interposed therebetween, and the second angular positions θ2 and the second angle positions θ2 and 123b with the convex surfaces 103b and 123b interposed therebetween. By providing the two bending angle positions θM2, the accelerations generated before and after the vane 131 passes through the inclined surfaces 104 and 124 can be offset. Then, by setting the acceleration to zero on the inclined surfaces 104 and 124, the acceleration can be reduced as a whole. Since the three vanes 131 rotate on the fixed body surfaces 100 and 120 in synchronization, the acceleration can be reduced for each of the three vanes 131, and the vibration caused by the acceleration can be suppressed as a whole.

(2) Specifically, inclined surfaces 104 and 124 are provided on both cam surfaces 103 and 123 to adjust the acceleration of the vanes 131 so that the accelerations of the three vanes 131 are always "positive", "negative" and "zero". I tried to take a combination. Therefore, even if both fixed body surfaces 100 and 120 have flat surfaces and acceleration is generated, the accelerations of the three vanes 131 can be canceled each other. As a result, vibration and noise caused by acceleration can be reduced.

(3) The positive acceleration when the vane 131 passes through the concave surfaces 103a and 123a is constant, and the negative acceleration when the vane 131 passes through the convex surfaces 103b and 123b is constant. Therefore, the shapes of the concave surfaces 103a, 123a and the convex surfaces 103b, 123b can be made into curved surfaces having a constant curvature, and the cam surfaces 103, 123 can be easily manufactured.

(4) On the cam surfaces 103 and 123, the time until the positive acceleration becomes constant, the time until the acceleration becomes zero, and the negative acceleration between the concave surfaces 103a and 123a and the inclined surfaces 104 and 124. The time until the acceleration becomes constant and the time until the acceleration becomes zero are the same. Further, the time when the positive acceleration is constant and the time when the negative acceleration is constant are the same. Therefore, the displacement pattern of the acceleration until the vane 131 passes through the concave surfaces 103a and 123a and reaches the inclined surfaces 104 and 124, and the acceleration until the vane 131 passes from the inclined surfaces 104 and 124 to the convex surfaces 103b and 123b. The displacement pattern can be made the same in opposite directions. Therefore, the positive acceleration and the negative acceleration can be canceled out to be zero, and the acceleration can be made zero in cooperation with the zero acceleration on the constant acceleration plane.

The above embodiment may be modified as follows. The above-described embodiment and the following alternative examples may be combined with each other within a technically consistent range. Further, regarding another example regarding the configuration on the front side, the corresponding configuration on the rear side can be changed in the same manner.

○ If the positive acceleration when passing through the concave surfaces 103a and 123a and the negative acceleration when passing through the convex surfaces 103b and 123b can be offset, the curvatures of the concave surfaces 103a and 123a and the curvatures of the convex surfaces 103b and 123b are different. You may. For example, the shapes of the concave surfaces 103a and 123a are set so that the displacement pattern of the acceleration of the vane 131 from the first front flat surface 101 through the front concave surface 103a to reach the front inclined surface 104 is a positive sine wave. do. On the other hand, the shapes of the convex surfaces 103b and 123b are set so that the displacement pattern of the acceleration from the front inclined surface 104 to the vane 131 passing through the front convex surface 103b and reaching the second front flat surface 102 is a negative sine wave. You may.

○ There is a slight difference between the time when the positive acceleration is constant when the vane 131 passes through the concave surfaces 103a and 123a and the time when the negative acceleration is constant when the vane 131 passes through the convex surfaces 103b and 123b. There may be.

○ The time required for the positive acceleration to become constant in the vane 131, the time required for the positive acceleration to become zero, the time required for the negative acceleration to become constant, and the time required for the negative acceleration to become zero. It may be slightly different from the time required for.

○ The rotating body surfaces 71a and 72a may be inclined with respect to the axial direction Z. In this case, both front flat surfaces 101, 102 and both rear flat surfaces 121, 122 may be flat surfaces orthogonal to the axial direction Z, or the rotating body surfaces 71a, so as to make surface contact with the rotating body surfaces 71a, 72a. It may be tilted at the same tilt angle as 72a.

○ A part of the rotating body cylinder portion 61 may be cut out or protruded. Further, the rotating body cylinder portion 61 has a cylindrical shape, but the present invention is not limited to this, and the rotating body tubular portion 61 may have a non-cylindrical shape. The fixed body insertion holes 91 and 111 may be formed so as to correspond to the shape of the rotating body cylinder portion 61 so that the gap between the inner wall surface thereof and the rotating body cylinder portion 61 becomes small, and are not limited to the circular shape. .. When a part of the rotating body cylinder portion 61 is cut out, another member may be fitted in the cutout portion.

The rotating body may have a disk shape having no portion protruding in the axial direction Z from the rotating body surfaces 71a and 72a, and may not be supported by both the fixed bodies 90 and 110. In this case, the front compression chamber A4 may be partitioned by the outer peripheral surface of the rotating shaft 12. That is, the front compression chamber A4 is not limited to the configuration defined by the outer peripheral surface 62 of the tubular portion, and may be partitioned by using the front rotating body surface 71a and the front fixed body surface 100. The same applies to the rear compression chamber A5.

○ The number of shaft bearings 51 and 53 is not limited to two, and may be one. For example, the rear shaft bearing 53 may be omitted. Further, three or more shaft bearings may be provided.
○ In the present embodiment, the accommodation chamber A3 is partitioned by the rear housing 22 and the rear plate 40, but the present invention is not limited to this, and the specific configuration for partitioning the accommodation chamber A3 is arbitrary.

For example, the compressor 10 may be configured to include a plate-shaped front plate instead of the rear housing 22, and a bottomed cylindrical rear cylinder instead of the rear plate 40. In this case, the accommodation chamber A3 is partitioned by abutting the rear cylinder and the front plate.

○ The bottom portion 23 of the rear housing and the side wall portion 24 of the rear housing may be separate bodies.
○ Both fixed bodies 90 and 110 have the same shape, but the shape is not limited to this, and for example, the front fixed body 90 may have a larger diameter than the rear fixed body 110, or vice versa. In this case, the inner peripheral surface 31 of the cylinder may have a stepped shape according to the shapes of both the fixed bodies 90 and 110, and the cylinder accommodating the front fixed body 90 and the cylinder accommodating the rear fixed body 110 may be formed. It may be provided separately. That is, the volumes of both compression chambers A4 and A5 may be the same or different.

○ The compressor 10 of the embodiment is provided with two compression chambers A4 and A5, but the present invention is not limited to this.
For example, the rear fixed body 110, the rear compression chamber A5, the rear suction port 150, and the rear discharge port 155 may be omitted. In this case, the first front flat surface 101 may be omitted on the front fixed body surface 100.

In such a configuration, for example, it is preferable to provide an urging portion for urging the vane 131 toward the front fixed body 90. The urging portion may be supported by, for example, an urging support portion provided on the rotating body cylinder portion 61 so that the urging portion can rotate with the rotation of the rotating body 60. The urging support portion is provided at, for example, the rear rotating body end portion 61b of the rotating body cylinder portion 61, and has a plate shape protruding outward in the radial direction R. As a result, the vane 131 rotates while moving in the axial direction Z while maintaining the state of being in contact with the front fixed body surface 100 as the rotating body 60 rotates. Instead of omitting the rear side configuration, the front side configuration may be omitted. In other words, there may be only one fixed body.

○ The fixed body insertion holes 91 and 111 do not have to be through holes as long as the rotating shaft 12 is inserted, and may be non-penetrating.
○ At least one of both thrust bearings 81 and 82 may be omitted. That is, the thrust bearings 81 and 82 are not essential.

○ At least one of the bearings of both rotating bodies may be omitted.
○ The specific shape of the housing 11 is arbitrary.
○ The specific shape of the rotating shaft 12 is arbitrary. For example, at least a part of the rotating shaft 12 may be formed in a hollow shape, or may be prismatic.

○ The electric motor 13 and the inverter 14 may be omitted. That is, the electric motor 13 and the inverter 14 are not essential in the compressor 10. In this case, the rotating shaft 12 may be rotated by, for example, belt driving.

Further, the rotating shaft 12 may be omitted as the electric motor 13 is omitted. In this case, for example, the rotating body 60 may be directly rotated by driving a belt or the like.
○ The compressor 10 may be used in addition to the air conditioner. For example, the compressor 10 may be used to supply compressed air to a fuel cell mounted on a fuel cell vehicle. That is, the fluid to be compressed by the compressor 10 is not limited to the refrigerant containing oil, and is arbitrary.

10 ... Compressor, 60 ... Rotating body, 71a, 72a ... Rotating body surface, 90, 110 ... Fixed body, 100, 120 ... Fixed body surface, 101, 102, 121, 122 ... Flat surface, 103, 123 ... Cam surface, 103a , 123a ... Concave surface as the first acceleration surface, 103b, 123b ... Convex surface as the second acceleration surface, 104, 124 ... Inclined surface as the constant acceleration surface, 130 ... Vane groove, 131 ... Vane, L ... Rotation axis, θ01 ... 1st intermediate angle position, θ02 ... 2nd intermediate angle position, θ1 ... 1st angle position, θ2 ... 2nd angle position, θ3 ... 3rd angle position, θ4 ... 4th angle position, θM1 ... 1st variation angle Position, θM2 ... Second variation angle position.

Claims (3)

A rotating body that rotates at a constant rotation speed around the rotation axis and has a rotating body surface that intersects the rotation axis.
A fixed body that does not rotate and has a fixed body surface that faces the rotating body surface and the axial direction in which the rotating axis extends.
It is provided with three vanes that are inserted into three vane grooves formed at positions shifted by 120 ° in the circumferential direction of the rotating body and that rotate while moving in the axial direction with the rotation of the rotating body.
The fixed body surface is
A pair of flat surfaces that intersect the axial direction and are displaced by 180 ° in the circumferential direction of the rotating body.
A pair of cam surfaces connecting the pair of flat surfaces are provided.
Assuming that the circumferential position on the fixed body surface is an angular position,
The intermediate angular position in the circumferential direction on one of the flat surfaces is defined as the first intermediate angular position.
The intermediate angular position in the circumferential direction on the other flat surface is defined as the second intermediate angular position.
The angular position of the boundary between each cam surface and one of the flat surfaces is set as the first angular position.
The angular position of the boundary between each cam surface and the other flat surface is set as the second angular position.
The angle position deviated by 60 ° from the first intermediate angle position is defined as the third angle position.
The angle position deviated by 120 ° from the first intermediate angle position is defined as the fourth angle position.
The angle position deviated from the third angle position to the first intermediate angle position side by the angle of the first angle position is defined as the first variation angle position.
The angle position deviated by the angle of the first angle position from the fourth angle position to the second intermediate angle position side is defined as the second variation angle position.
The angle position deviated by the angle of the first angle position from the second angle position to the second intermediate angle position side becomes the second intermediate angle position.
The velocity change when the vane moves in the axial direction is defined as the acceleration of the vane, and the velocity change when the vane moves in the positive direction approaching the fixed body surface relative to the rotating body surface is a positive acceleration. When the velocity change when the vane moves in the negative direction away from the fixed body surface relative to the rotating body surface is defined as a negative acceleration.
Each cam surface
A first acceleration surface located between the first angular position and the first inflection point position to generate the positive acceleration,
A second acceleration surface located between the second angle position and the second inflection point position to generate the negative acceleration,
It has an acceleration constant surface that is located between the first inflection angle position and the second inflection angle position and makes the acceleration zero.
On the fixed body surface, the one flat surface, the first acceleration surface, the constant acceleration surface, the second acceleration surface, and the other flat surface are arranged continuously in the circumferential direction in the above order. A compressor characterized by being. The compressor according to claim 1, wherein the positive acceleration when the vane passes through the first acceleration surface is constant, and the negative acceleration when the vane passes through the second acceleration surface is constant. The time required for the positive acceleration to become constant, the time required for the positive acceleration to become zero, the time required for the negative acceleration to become constant, and the time required for the negative acceleration to become zero. The compressor according to claim 2, wherein the required time is the same, and the time when the positive acceleration is constant and the time when the negative acceleration is constant are the same.

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